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EP0223704B1 - Electric brake unit for a vehicle - Google Patents

Electric brake unit for a vehicle Download PDF

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Publication number
EP0223704B1
EP0223704B1 EP86402517A EP86402517A EP0223704B1 EP 0223704 B1 EP0223704 B1 EP 0223704B1 EP 86402517 A EP86402517 A EP 86402517A EP 86402517 A EP86402517 A EP 86402517A EP 0223704 B1 EP0223704 B1 EP 0223704B1
Authority
EP
European Patent Office
Prior art keywords
control shaft
piston means
actuating
friction member
electric motor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP86402517A
Other languages
German (de)
French (fr)
Other versions
EP0223704A1 (en
Inventor
Jean-Jacques Carre
Alain Thioux
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bendix France SA
Original Assignee
Bendix France SA
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bendix France SA filed Critical Bendix France SA
Publication of EP0223704A1 publication Critical patent/EP0223704A1/en
Application granted granted Critical
Publication of EP0223704B1 publication Critical patent/EP0223704B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
    • F16D65/567—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc brake
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60T—VEHICLE BRAKE CONTROL SYSTEMS OR PARTS THEREOF; BRAKE CONTROL SYSTEMS OR PARTS THEREOF, IN GENERAL; ARRANGEMENT OF BRAKING ELEMENTS ON VEHICLES IN GENERAL; PORTABLE DEVICES FOR PREVENTING UNWANTED MOVEMENT OF VEHICLES; VEHICLE MODIFICATIONS TO FACILITATE COOLING OF BRAKES
    • B60T13/00—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems
    • B60T13/74—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive
    • B60T13/741—Transmitting braking action from initiating means to ultimate brake actuator with power assistance or drive; Brake systems incorporating such transmitting means, e.g. air-pressure brake systems with electrical assistance or drive acting on an ultimate actuator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/025—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members with two or more rotating discs at least one of them being located axially
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/14—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position
    • F16D65/16—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake
    • F16D65/18—Actuating mechanisms for brakes; Means for initiating operation at a predetermined position arranged in or on the brake adapted for drawing members together, e.g. for disc brakes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D66/00—Arrangements for monitoring working conditions, e.g. wear, temperature
    • F16D2066/005—Force, torque, stress or strain
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2121/00—Type of actuator operation force
    • F16D2121/18—Electric or magnetic
    • F16D2121/24—Electric or magnetic using motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
    • F16D2125/34—Mechanical mechanisms converting rotation to linear movement or vice versa acting in the direction of the axis of rotation
    • F16D2125/40—Screw-and-nut
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/58—Mechanical mechanisms transmitting linear movement
    • F16D2125/582—Flexible element, e.g. spring, other than the main force generating element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/58—Mechanical mechanisms transmitting linear movement
    • F16D2125/582—Flexible element, e.g. spring, other than the main force generating element
    • F16D2125/585—Flexible element, e.g. spring, other than the main force generating element arranged in parallel with a force-applying member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2125/00—Components of actuators
    • F16D2125/18—Mechanical mechanisms
    • F16D2125/58—Mechanical mechanisms transmitting linear movement
    • F16D2125/66—Wedges

Definitions

  • the present invention relates to electric braking devices for vehicles, of the type comprising an actuating mechanism for moving in one direction at least one friction member and bringing it into friction engagement with at least one rotary member to be braked, the mechanism actuator comprising an electric motor driving in rotation a control shaft comprising a threaded part cooperating in reversible drive engagement with an actuator movable linearly to actuate the friction member.
  • an electric braking device of this type is described in document FR-A-2 557 528.
  • the actuating member, actuated by the control shaft is constituted in the form of a screw attacking a pressure lever articulated on a support piece and coupled to the friction member, according to a delicate construction and implementation arrangement, imposing a particular structure on the whole of the braking device, and having a low yield high requiring considerable electrical power.
  • the object of the present invention is to provide a braking device for vehicles of the type under consideration, of simple and robust design, low manufacturing costs, imposing only slight general modifications on the entire braking device, having a yield improved, consequently requiring reduced electrical power and suitable for a large number of different uses for a wide range of vehicles.
  • control shaft extends substantially orthogonally to said direction of movement of the friction member
  • the actuating member comprising a wedge structure associated with at least a pair of rollers cooperating respectively with a pair of facing ramp surfaces of which at least a first ramp surface is formed on a piston means movable in said direction to actuate the friction member and the braking comprising at least one axial ball stop means between the control shaft and an adjacent stationary wall.
  • the arrangement according to the invention makes it possible, on the one hand, to easily arrange the actuation mechanism in a general brake structure of conventional design as described in document US-A 4,064,973 and, on the other hand , to obtain, in a reduced overall volume, an improved yield allowing its use in a wide range of vehicles.
  • the rotary member to be braked consists of at least one disc, advantageously two, the braking device comprising a caliper structure overlapping the disc and supporting the mechanism actuation, the piston means sliding in a bore formed in the caliper structure, which can thus be derived directly from a caliper structure of a conventional braking device with hydraulic or hydraulic-mechanical operation.
  • caliper 2 In the structure of caliper 2 are mounted to guide and slide the friction members 4A, 4B, 4C movable in a direction parallel to the axis of rotation of the discs 1a, and 1 directly, and indirectly by reaction through the caliper structure 2 , by a piston means, generally designated by the reference 5 sliding in a bore 6 formed in the caliper structure and with an axis parallel to the axis of rotation of the discs 1a, 1b.
  • the bore 6 opens into a well 7 formed transversely in the stirrup structure 2 and on the outer end of which is attached an electric motor 8.
  • the output shaft 9 of the electric motor 8 is coupled in rotation to a shaft of control 10 extending in the well 7 in a direction substantially orthogonal to the axis of the bore 6 (in fact, at an angle of about 85 ° relative to this axis).
  • the control shaft has a threaded main end portion 11 on which is engaged in reversible engagement a wedge structure 12 internally threaded with which is associated a cage 13 carrying at least one pair of rollers with parallel axes 14 cooperating respectively in engagement bearing and rolling, with a pair of facing ramp surfaces 15 and 16 converging in the direction of convergence of the external corner surfaces of the corner structure 12.
  • a first (15) of these surfaces ramps is formed by the inner face of the piston structure 5 opening into the well 7, the second (16) of these ramp surfaces being formed by a block 17 mounted in the zone of the well 7 opposite the bore 6.
  • the unthreaded end of the control shaft 10 is coupled to the tree outlet 9 by an elastic coupling 18 of the elastic ring type secured to two metal flanges coupled respectively to the shafts 9 and 10.
  • a spherical cage of a ball bearing generally designated by the reference 19, whose stationary cage, also having a spherical central portion, is constituted by a partition 20, crossed by the control shaft 10 and clamped between the mounting flange of the electric motor 8 and a flange of end of the portion of the stirrup structure 2 defining the well 7.
  • a compression spring 21, bearing on a flange 22 supported on the control shaft 10 biases the cage 13 carrying the rollers 14 in the direction tending to maintain the latter in contact against the ramp surfaces 15 and 16, and against the associated spacing faces of the corner structure 12.
  • an assistance spring 50 of force (for example 40 daN) greater than that of the spring 21, is disposed between the partition 20 and the flange 22 , pressing it against the adjacent end of the corner structure 12 and therefore normally biasing the latter in the direction of actuation under braking.
  • the assistance spring 50 compressed in the rest position, provides a good part of the braking force, the full power of the motor 8 being only required for the obtaining a maximum braking force (up to 60 daN).
  • the return of the corner structure 12 to its rest position is used to compress the assistance spring 50 which will thus be fully operational again for the subsequent braking phase.
  • a force or pressure sensor 23 for example of the piezoelectric type or with strain gauge, for detecting , by reaction, the force exerted by the piston structure 5 on the friction members 4 and, consequently, the braking force exerted by the wedge structure 12, thus allowing precise control of the engine 9 in both directions actuation.
  • the electric signals coming from the force sensor 23 are transmitted to an electronic control unit 24 also receiving signals coming from a position or force sensor 25 associated with the brake pedal 26 of the vehicle and generating the control signal, transmitted by a line 27, of the electric motor 8 for the application of the brake.
  • the piston means 5 incorporates a backlash system, generally designated by the reference 28, as described for example in relation to FIG. 5 of document EP-A-0145535, the content is assumed to be incorporated here for reference and incorporating a central screw 29 directly actuating the adjacent friction member 4a and axially adjustable relative to the main structure of the piston means 5 which forms the rear ramp surface 15 and which is recalled in the direction of engagement with the adjacent roller 14 by a pair of springs 30 and 31, coaxial with the axis of the bore 6, of the clearance take-up system 28.
  • a backlash system generally designated by the reference 28, as described for example in relation to FIG. 5 of document EP-A-0145535, the content is assumed to be incorporated here for reference and incorporating a central screw 29 directly actuating the adjacent friction member 4a and axially adjustable relative to the main structure of the piston means 5 which forms the rear ramp surface 15 and which is recalled in the direction of engagement with the adjacent roller 14 by a pair of springs 30 and 31, coaxial with the axis of the bore 6, of the
  • a braking device with a single disc, typically implements an electric motor 8 with a power of 115 watts at 5500 rpm with a pulse torque of 1 mN.
  • the electric motor 8 can have a significantly reduced power.
  • the present invention is also applicable to drum brakes, the ramp surfaces 15 and 16 then being formed by the opposite ends of two opposite and coaxial piston means, the force or pressure sensor 23 being integrated in one of these pistons.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Braking Arrangements (AREA)

Description

La présente invention concerne les dispositifs de freinage électrique pour véhicules, du type comprenant un mécanisme d'actionnement pour déplacer dans une direction au moins un organe de friction et l'amener en engagement de friction avec au moins un organe rotatif à freiner, le mécanisme d'actionnement comprenant un moteur électrique entraînant en rotation un arbre de commande comportant une partie filetée coopérant en engagement d'entraînement réversible avec un organe d'actionnement déplaçable linéairement pour actionner l'organe de friction.The present invention relates to electric braking devices for vehicles, of the type comprising an actuating mechanism for moving in one direction at least one friction member and bringing it into friction engagement with at least one rotary member to be braked, the mechanism actuator comprising an electric motor driving in rotation a control shaft comprising a threaded part cooperating in reversible drive engagement with an actuator movable linearly to actuate the friction member.

Un dispositif de freinage électrique de ce type est décrit dans le document FR-A-2 557 528. Dans le dispositif de ce document, l'organe d'actionnement, actionné par l'arbre de commande, est constitué sous la forme d'une vis attaquant un levier de pression articulé sur une pièce support et couplé l'organe de friction, suivant un agencement de construction et de mise en oeuvre délicates, imposant une structure particulière à l'ensemble du dispositif de freinage, et présentant un rendement peu élevé nécessitant une puissance électrique considérable.An electric braking device of this type is described in document FR-A-2 557 528. In the device of this document, the actuating member, actuated by the control shaft, is constituted in the form of a screw attacking a pressure lever articulated on a support piece and coupled to the friction member, according to a delicate construction and implementation arrangement, imposing a particular structure on the whole of the braking device, and having a low yield high requiring considerable electrical power.

Un autre dispositif de freinage électrique, présentant les caractéristiques contenues dans la premier part de la revendication 1 est décrit dans le document GB-A 2 156 021.Another electric braking device, having the characteristics contained in the first part of claim 1 is described in document GB-A 2 156 021.

La présente invention a pour objet de proposer un dispositif de freinage pour véhicules du type considéré, de conception simple et robuste, de faibles coûts de fabrication, n'imposant à l'ensemble du dispositif de freinage que de faibles modifications générales, présentant un rendement amélioré, requérant en conséquence une puissance électrique réduite et convenant à un grand nombre d'utilisations différentes pour une large gamme de véhicules.The object of the present invention is to provide a braking device for vehicles of the type under consideration, of simple and robust design, low manufacturing costs, imposing only slight general modifications on the entire braking device, having a yield improved, consequently requiring reduced electrical power and suitable for a large number of different uses for a wide range of vehicles.

Pour ce faire, selon une caractéristique de l'invention, l'arbre de commande s'étend sensiblement orthogonalement à la dite direction de déplacement de l'organe de friction, l'organe d'actionnement comprenant une structure de coin associée à au moins une paire de galets coopérant respectivement avec une paire de surfaces de rampes en vis- à- vis dont au moins une première surface de rampe est formée sur un moyen de piston déplaçable dans la dite direction pour actionner l'organe de friction et le dispositif de freinage comprenant au moins un moyen de butée axiale à bille entre l'arbre de commande et une paroi stationnaire adjacente.To do this, according to a characteristic of the invention, the control shaft extends substantially orthogonally to said direction of movement of the friction member, the actuating member comprising a wedge structure associated with at least a pair of rollers cooperating respectively with a pair of facing ramp surfaces of which at least a first ramp surface is formed on a piston means movable in said direction to actuate the friction member and the braking comprising at least one axial ball stop means between the control shaft and an adjacent stationary wall.

L'agencement selon l'invention permet, d'une part, d'aménager aisément le mécanisme d'actionnement dans une structure générale de frein de conception classique tel que décrit dans le document US-A 4 064 973 et, d'autre part, d'obtenir, dans un volume global réduit, un rendement amélioré permettant son utilisation dans une large gammme de véhicules.The arrangement according to the invention makes it possible, on the one hand, to easily arrange the actuation mechanism in a general brake structure of conventional design as described in document US-A 4,064,973 and, on the other hand , to obtain, in a reduced overall volume, an improved yield allowing its use in a wide range of vehicles.

Dans cet esprit, selon une autre caractéristique de l'invention, l'organe rotatif à freiner est constitué d'au moins un disque, avantageusement deux, le dispositif de freinage comportant une structure d'étrier chevauchant le disque et supportant le mécanisme d'actionnement, le moyen de piston coulissant dans un alésage formé dans la structure d'étrier, laquelle peut ainsi être dérivée directement d'une structure d'étrier de dispositif de freinage classique à fonctionnement hydraulique ou hydraulique-mécanique.In this spirit, according to another characteristic of the invention, the rotary member to be braked consists of at least one disc, advantageously two, the braking device comprising a caliper structure overlapping the disc and supporting the mechanism actuation, the piston means sliding in a bore formed in the caliper structure, which can thus be derived directly from a caliper structure of a conventional braking device with hydraulic or hydraulic-mechanical operation.

D'autres caractéristiques et avantages de la présente invention ressortiront de la description suivante d'un mode de réalisation, donné à titre illustratif mais nullement limitatif, faite en relation avec les dessins annexés, sur lesquels :

  • la figure 1, est une vue en coupe schématique d'un dispositif de freinage électrique selon l'invention ; et
  • La fig. 2 est une vue similaire d'un autre mode de réalisation de l'invention.
Other characteristics and advantages of the present invention will emerge from the following description of an embodiment, given by way of illustration but in no way limiting, made in relation to the appended drawings, in which:
  • Figure 1 is a schematic sectional view of an electric braking device according to the invention; and
  • Fig. 2 is a similar view of another embodiment of the invention.

Dans le mode de réalisation représenté sur la figure 1, on reconnait un dispositif de freinage à disques du type général décrit dans le document EP-A-0117 192, dont le contenu est supposé intégré ici pour référence et comprenant une paire de disques parallèles 1 a, 1b, couplés à une roue de véhicule (non représentée) et chevauchés par une structure d'étrier, désignée généralement par la référence 2, montée avec possibilité de coulissement sur un support fixe repéré par la référence 3. Dans la structure d'étrier 2 sont montés à guidage et à coulissement des organes de friction 4A, 4B, 4C déplaçables dans une direction parallèle à l'axe de rotation des disques 1a, et 1 directement, et indirectement par réaction au travers de la structure d'étrier 2, par un moyen de piston, désigné généralement par la référence 5 coulissant dans un alésage 6 formé dans la structure d'étrier et d'axe parallèle à l'axe de rotation des disques 1 a, 1b. L'alésage 6 débouche dans un puits 7 formé transversalement dans la structure d'étrier 2 et sur l'extrémité extérieure duquel est rapporté un moteur électrique 8. L'arbre de sortie 9 du moteur électrique 8 est couplé en rotation à un arbre de commande 10 s'étendant dans le puits 7 dans une direction sensiblement orthogonale à l'axe de l'alésage 6 (en fait, suivant un angle d'environ 85° par rapport à cet axe). L'arbre de commande comporte une partie d'extrémité principale filetée 11 sur laquelle est engagée en engrènement réversible une structure de coin 12 taraudée intérieurement à laquelle est associée une cage 13 portant au moins une paire de galets à axes parallèles 14 coopérant respectivement en engagement d'appui et de roulement, avec une paire de surfaces de rampes en vis-à-vis 15 et 16 convergeant dans la direction de convergence des surfaces de coin externes de la structure de coin 12. Une première (15) de ces surfaces de rampes est formée par la face intérieure de la structure de piston 5 débouchant dans le puits 7, la seconde (16) de ces surfaces de rampes étant formée par un bloc 17 monté dans la zone du puits 7 opposée à l'alésage 6.In the embodiment shown in FIG. 1, there is a disc braking device of the general type described in document EP-A-0117 192, the content of which is assumed to be integrated here for reference and comprising a pair of parallel discs 1 a, 1b, coupled to a vehicle wheel (not shown) and overlapped by a caliper structure, generally designated by the reference 2, mounted with the possibility of sliding on a fixed support identified by the reference 3. In the structure of caliper 2 are mounted to guide and slide the friction members 4A, 4B, 4C movable in a direction parallel to the axis of rotation of the discs 1a, and 1 directly, and indirectly by reaction through the caliper structure 2 , by a piston means, generally designated by the reference 5 sliding in a bore 6 formed in the caliper structure and with an axis parallel to the axis of rotation of the discs 1a, 1b. The bore 6 opens into a well 7 formed transversely in the stirrup structure 2 and on the outer end of which is attached an electric motor 8. The output shaft 9 of the electric motor 8 is coupled in rotation to a shaft of control 10 extending in the well 7 in a direction substantially orthogonal to the axis of the bore 6 (in fact, at an angle of about 85 ° relative to this axis). The control shaft has a threaded main end portion 11 on which is engaged in reversible engagement a wedge structure 12 internally threaded with which is associated a cage 13 carrying at least one pair of rollers with parallel axes 14 cooperating respectively in engagement bearing and rolling, with a pair of facing ramp surfaces 15 and 16 converging in the direction of convergence of the external corner surfaces of the corner structure 12. A first (15) of these surfaces ramps is formed by the inner face of the piston structure 5 opening into the well 7, the second (16) of these ramp surfaces being formed by a block 17 mounted in the zone of the well 7 opposite the bore 6.

Pour permettre un léger débattement angulaire de l'arbre de commande 10 par rapport à l'arbre de sortie 9 du moteur électrique 8 pour accompagner le déplacement du moyen de piston 5, l'extrémité non filetée de l'arbre de commande 10 est couplée à l'arbre de sortie 9 par un accouplement élastique 18 du type à anneau élastique solidarisé à deux flasques métalliques couplés respectivement aux arbres 9 et 10. Sur la portion non filetée de l'arbre de commande 10 est montée une cage sphérique d'une butée à billes, désignée généralement par la référence 19, dont la cage stationnaire, présentant également une portion centrale sphérique, est constituée par une cloison 20, traversée par l'arbre de commande 10 et bridée entre la bride de montage du moteur électrique 8 et un flasque d'extrémité de la portion de la structure d'étrier 2 définissant le puits 7. Un ressort de compression 21, prenant appui sur une collerette 22 supportée sur l'arbre de commande 10 sollicite la cage 13 portant les galets 14 dans la direction tendant à maintenir ces derniers en contact contre les surfaces de rampes 15 et 16, et contre les faces d'écartement associées de la structure de coin 12.To allow a slight angular movement of the control shaft 10 relative to the output shaft 9 of the electric motor 8 to accompany the movement of the piston means 5, the unthreaded end of the control shaft 10 is coupled to the tree outlet 9 by an elastic coupling 18 of the elastic ring type secured to two metal flanges coupled respectively to the shafts 9 and 10. On the unthreaded portion of the control shaft 10 is mounted a spherical cage of a ball bearing, generally designated by the reference 19, whose stationary cage, also having a spherical central portion, is constituted by a partition 20, crossed by the control shaft 10 and clamped between the mounting flange of the electric motor 8 and a flange of end of the portion of the stirrup structure 2 defining the well 7. A compression spring 21, bearing on a flange 22 supported on the control shaft 10 biases the cage 13 carrying the rollers 14 in the direction tending to maintain the latter in contact against the ramp surfaces 15 and 16, and against the associated spacing faces of the corner structure 12.

On comprendra qu'une rotation dans un sens de l'arbre de commande 10 provoque un déplacement du coin 12, et des galets 14 associés, dans une direction provoquant un écartement relatif des surfaces de rampes 15 et 16 et, donc un déplacement de la structure de piston 5 dans la direction amenant en engagement de friction les organes de friction 4 avec les disques 1 , tandis qu' une rotation dans l'autre sens de l'arbre de commande 10 ramènera l'ensemble de la structure de coin 12 et des galets 14 vers la configuration de repos représentée sur la figure.It will be understood that a rotation in one direction of the control shaft 10 causes a displacement of the wedge 12, and the associated rollers 14, in a direction causing a relative spacing of the ramp surfaces 15 and 16 and, therefore, a displacement of the piston structure 5 in the direction bringing in friction engagement the friction members 4 with the discs 1, while a rotation in the other direction of the control shaft 10 will bring back the whole of the wedge structure 12 and rollers 14 to the rest configuration shown in the figure.

Selon un aspect avantageux de l'invention, comme on le voit sur la Figure 2, un ressort d'assistance 50, de force (par exemple 40 daN) supérieure à celle du ressort 21, est disposé entre la cloison 20 et la collerette 22, plaquant celle-ci contre l'extrémité adjacente de la structure de coin 12 et sollicitant donc normalement cette dernière dans la direction d'actionnement en freinage. Ainsi, lors du commencement d'une phase de freinage, le ressort d'assistance 50,comprimé en position de repos, fournit une bonne part de l'effort de freinage, la pleine puissance du moteur 8 n'étant requise que pour l'obtention d'un effort de freinage maximum (jusqu'à 60 daN). Par contre, à chaque phase de défreinage, lorsque le moteur n'a plus à exercer l'effort de freinage, le retour de la structure de coin 12 vers sa position de repos est mis à profit pour récomprimer le ressort d'assistance 50 qui sera ainsi de nouveau pleinement opérationnel pour la phase de freinage subséquente.According to an advantageous aspect of the invention, as can be seen in FIG. 2, an assistance spring 50, of force (for example 40 daN) greater than that of the spring 21, is disposed between the partition 20 and the flange 22 , pressing it against the adjacent end of the corner structure 12 and therefore normally biasing the latter in the direction of actuation under braking. Thus, at the start of a braking phase, the assistance spring 50, compressed in the rest position, provides a good part of the braking force, the full power of the motor 8 being only required for the obtaining a maximum braking force (up to 60 daN). On the other hand, at each brake release phase, when the engine no longer has to exert the braking force, the return of the corner structure 12 to its rest position is used to compress the assistance spring 50 which will thus be fully operational again for the subsequent braking phase.

Selon un autre aspect de l'invention, entre le bloc stationnaire 17 et son support dans la structure d'étrier 2 est disposé un capteur de force ou de pression 23, par exemple du type piézo-électrique ou à jauge de contraintes, pour détecter, par réaction, la force exercée par la structure de piston 5 sur les organes de friction 4 et, partant, l'effort de freinage exercé par la structure de coin 12, permettant ainsi un pilotage précis du moteur 9 dans les deux sens d'actionnement. Les signaux électriques provenant du capteur de force 23 sont transmis à une unité de commande électronique 24 recevant également des signaux en provenance d'un capteur de position ou de force 25 associé à la pédale de freins 26 du véhicule et élaborant le signal de commande, transmis par une ligne 27, du moteur électrique 8 pour la mise en oeuvre du frein.According to another aspect of the invention, between the stationary block 17 and its support in the stirrup structure 2 is arranged a force or pressure sensor 23, for example of the piezoelectric type or with strain gauge, for detecting , by reaction, the force exerted by the piston structure 5 on the friction members 4 and, consequently, the braking force exerted by the wedge structure 12, thus allowing precise control of the engine 9 in both directions actuation. The electric signals coming from the force sensor 23 are transmitted to an electronic control unit 24 also receiving signals coming from a position or force sensor 25 associated with the brake pedal 26 of the vehicle and generating the control signal, transmitted by a line 27, of the electric motor 8 for the application of the brake.

Selon une autre caractéristique de l'invention, le moyen de piston 5 incorpore un système de rattrapage de jeux, désigné généralement par la référence 28, tel que décrit par exemple en relation avec la figure 5 du document EP-A-0145535, dont le contenu est supposé intégré ici pour référence et incorporant une vis centrale 29 actionnant directement l'organe de friction adjacent 4a et réglable axialement par rapport à la structure principale du moyen de piston 5 qui forme la surface de rampe arrière 15 et qui est rappelée dans la direction d'engagement avec le galet adjacent 14 par une paire de ressort 30 et 31, coaxiaux l'axe de l'alésage 6, du système de rattrapage de jeux 28.According to another characteristic of the invention, the piston means 5 incorporates a backlash system, generally designated by the reference 28, as described for example in relation to FIG. 5 of document EP-A-0145535, the content is assumed to be incorporated here for reference and incorporating a central screw 29 directly actuating the adjacent friction member 4a and axially adjustable relative to the main structure of the piston means 5 which forms the rear ramp surface 15 and which is recalled in the direction of engagement with the adjacent roller 14 by a pair of springs 30 and 31, coaxial with the axis of the bore 6, of the clearance take-up system 28.

Selon le type de véhicule, un dispositif de freinage selon l'invention, avec un disque unique, met en oeuvre typiquement un moteur électrique 8 d'une puissance de 115 watts à 5500 tours/minute avec un couple impulsionnel de 1 mN.Depending on the type of vehicle, a braking device according to the invention, with a single disc, typically implements an electric motor 8 with a power of 115 watts at 5500 rpm with a pulse torque of 1 mN.

Dans les modes de réalisation avec une paire de disques parallèles 1a, 1 b et un ressort d'assistance 50 , le moteur électrique 8 peut avoir une puissance notablement réduite. La présente invention est également applicable à des freins à tambour, les surfaces de rampes 15 et 16 étant alors formées par les extrémités en regard de deux moyens de pistons coaxiaux et opposés, le capteur de force ou de pression 23 étant intégré dans un de ces pistons.In the embodiments with a pair of parallel disks 1a, 1b and an assistance spring 50, the electric motor 8 can have a significantly reduced power. The present invention is also applicable to drum brakes, the ramp surfaces 15 and 16 then being formed by the opposite ends of two opposite and coaxial piston means, the force or pressure sensor 23 being integrated in one of these pistons.

Claims (9)

1. Electrical braking device for a vehicle, comprising an actuating mechanism for displacing at least one friction member (4a) in one direction and for bringing it into frictional engagement with at least one rotary member to be braked (1 a), the actuating mechanism comprising an electric motor (8) which drives in reversible rotation a control shaft (10) having a threaded part (11) cooperating in driving engagement with an actuating member (12) displaceable linearly to actuate the friction member, characterized in that the control shaft (10) extends substantially at right angle to the said direction of displacement of the friction member, and in that the actuating member comprises a wedge structure (12) associated with at least one pair of rollers (14) cooperating respectively with a pair of opposing ramp surfaces (15, 16), at least a first (15) of these ramp surfaces being formed on a piston means (5) displaceable in the said direction to actuate the friction member (4a), and in that it comprises at least one axial ball thrust-bearing means (19) between the control shaft (10) and an adjacent stationary wall (20), to absorb the axial forces on the control shaft (10) and allow a slight angular deflection of the control shaft (10) to accompany the displacement of the piston means (5).
2. Device according to Claim 1, characterized in that it comprises an assistance spring (50) biasing the wedge structure (12) in the actuating direction of the piston means (5).
3. Device according to either of Claims 1 or 2, characterized in that the control shaft (10) is connected to the output shaft (9) of the electric motor (8) via an elastic coupling (18).
4. Device according to any of Claims 1 to 3, characterized in that it comprises at least one force sensor device (23) associated with at least one (16) of said ramp surfaces.
5. Device according to any of the preceding claims, characterized in that the rotary member comprises at least one disc (1 a), the device including a caliper structure (2) straddling the disc and supporting the actuating mechanism, said piston means (5) sliding in a bore (6) formed in the caliper structure (2).
6. Device according to Claim 5, characterized in that the second ramp surface (16) is mounted stationary in the caliper structure (2).
7. Device according to Claim 4 and Claim 6, characterized in that the force sensor device is associated with the second ramp surface (16).
8. Device according to any of Claims 5 to 7, characterized in that the rotary member comprises two parallel discs (1 a, 1b).
9. Device according to any of Claims 5 to 8, characterized in that the piston means (5) includes a system (28) for compensating functional plays.
EP86402517A 1985-11-20 1986-11-12 Electric brake unit for a vehicle Expired - Lifetime EP0223704B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8517180 1985-11-20
FR8517180A FR2590219B1 (en) 1985-11-20 1985-11-20 ELECTRIC BRAKING DEVICE FOR VEHICLE

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EP0223704A1 EP0223704A1 (en) 1987-05-27
EP0223704B1 true EP0223704B1 (en) 1990-06-13

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EP86402517A Expired - Lifetime EP0223704B1 (en) 1985-11-20 1986-11-12 Electric brake unit for a vehicle

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US (1) US4784244A (en)
EP (1) EP0223704B1 (en)
JP (1) JP2657913B2 (en)
KR (1) KR870005196A (en)
DE (1) DE3671945D1 (en)
ES (1) ES2015268B3 (en)
FR (1) FR2590219B1 (en)

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Also Published As

Publication number Publication date
JPS62127533A (en) 1987-06-09
FR2590219B1 (en) 1991-02-01
DE3671945D1 (en) 1990-07-19
FR2590219A1 (en) 1987-05-22
ES2015268B3 (en) 1990-08-16
US4784244A (en) 1988-11-15
JP2657913B2 (en) 1997-09-30
KR870005196A (en) 1987-06-05
EP0223704A1 (en) 1987-05-27

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